CN102865359A - Hydraulic actuation device for actuating positioning members in motor vehicle transmission - Google Patents

Hydraulic actuation device for actuating positioning members in motor vehicle transmission Download PDF

Info

Publication number
CN102865359A
CN102865359A CN2012102345356A CN201210234535A CN102865359A CN 102865359 A CN102865359 A CN 102865359A CN 2012102345356 A CN2012102345356 A CN 2012102345356A CN 201210234535 A CN201210234535 A CN 201210234535A CN 102865359 A CN102865359 A CN 102865359A
Authority
CN
China
Prior art keywords
piston
cylinder assembly
pump
hydraulic
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN2012102345356A
Other languages
Chinese (zh)
Other versions
CN102865359B (en
Inventor
W·赫伯那
S·伦克
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FTE Automotive GmbH
Original Assignee
FTE Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by FTE Automotive GmbH filed Critical FTE Automotive GmbH
Publication of CN102865359A publication Critical patent/CN102865359A/en
Application granted granted Critical
Publication of CN102865359B publication Critical patent/CN102865359B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/12—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action
    • F15B11/121—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions
    • F15B11/122—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor providing distinct intermediate positions; with step-by-step action providing distinct intermediate positions by means of actuators with multiple stops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/34—Locking or disabling mechanisms
    • F16H63/3416—Parking lock mechanisms or brakes in the transmission
    • F16H63/3483—Parking lock mechanisms or brakes in the transmission with hydraulic actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/48—Signals to a parking brake or parking lock; Control of parking locks or brakes being part of the transmission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F15B2211/7054—Having equal piston areas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/72—Output members, e.g. hydraulic motors or cylinders or control therefor having locking means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H2061/004—Venting trapped air from hydraulic systems

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Transmission Device (AREA)

Abstract

An actuating device for hydraulically actuating at least one setting element comprising a pump, which has an electric pump drive, with reversible pumping direction, at least one double-acting piston-cylinder arrangement, which is connected therewith and the piston of which is operatively connected with the setting element, and a hydraulic fluid reservoir from which the hydraulic fluid can be pumped to the piston-cylinder arrangement in order to hydraulically load the piston thereof for a setting element movement depending on pumping direction on one (effective surface 22) or other (effective surface 24) side. In this connection, the piston-cylinder arrangement is functionally associated with a detent device with a blocking element, which is spring-biased into a blocking position preventing setting element movement and is movable by an electrically activatable actuator from the blocking position into a release position permitting setting element movement. In addition, a pump driver and an execution mechanism are in connection with a control unit which coordinates electric power active action of the components.

Description

Be used for driving the hydraulic transmission of motor vehicle transmission positioning element
Technical field
According to claim 1, preamble the present invention relates to a kind of hydraulic transmission.The invention particularly relates to be used to the hydraulic transmission that drives one or more positioning elements, for example, the transmission device transmission component in the motor vehicle transmission, the transmission device of described motor vehicle transmission is widely used in the modern automotive vehicle.
Background technique
Mentioned transmission device transmission component, normally with or not shifting fork and the speed changer sleeve of tape synchronizer, be used for automatic shifting transmission gear box (ASG), double clutch or multi-clutch speed changer (TCT) and separable power splitter speed change gear and transaxle.The driving of these parts is by motor machine or hydraulically powered, and wherein, hydraulic driving is with respect to the advantage of the physical configuration in the speed changer high power density of actuator due to.Therefore, shifting fork or speed changer sleeve can be driven directly, and avoid by the extra friction loss that produces such as the mechanical motion driving mechanism.The configuration of this speed changer also has the advantage that adapts to installing space with respect to the motor machine drive system, described motor machine drive system usually reaches outside the external frame of speed changer, thereby hinders the installation of speed changer in the motor vehicle.
Known hydraulic transmission is (for example, referring to Fig. 1 of DEA-4309901; Figure 27 of DE-A-19637001; Figure 11 F of DE-A-19950443), generally include generation or pumping and store unit (so-called " (PCC) power "), the valve block of pressure, pipeline and actuator or the cylinder itself of fluid transfer, also comprise alternatively for the integrated transducer system that determines the transmission element position; Described valve block can by the valve of motor machine driving, be used for hydraulic energy is assigned to each actuator with some.Hydraulic transmission in the motor vehicle transmission usually activates by transmission control unit or upper vehicle computer.
The sort of hydraulic transmission with storage unit a shortcoming arranged, exactly in order to load described storage unit, pressure medium, namely the pumping pressure level of hydraulic fluid is had to the maximum pressure far above actuator's actual demand, in order to necessary working pressure still can be provided after having aspirated needed amount, this causes the loss of energy, and has reduced widely the efficient of device.In addition, the main structure of solenoid valve is guiding valve, because its closely tolerance clearance, highly fluid and forced filtration measure of cleaning.Yet used guiding valve has the leakage of trace, and through the corresponding operation cycle, this leakage causes the storage unit complete discharge, and the result causes the time that postpones load store unit that drives first.In addition, in the situation that drive without speed change gear, for example, on expressway, need to reload to storage unit at regular intervals, this causes the loss of energy equally.At last, occupy a large amount of installing spaces with the valve group of solenoid valve in speed changer, this is representing the cost factor of described transmission device maximum.
At last, a kind of EP-A-0706052 hydraulic transmission that derives from, be used for driving the transmission device transmission component (shifting fork) of motor vehicle transmission, form claim 1 preamble (Fig. 1), comprise pump, described pump has the reversible motor-drive pump driver (being referred to as reversible pump) of pumping direction; Double-acting piston-cylinder assembly, described piston-cylinder assembly hydraulic connecting is to described pump, the piston of described piston-cylinder assembly is connected to the transmission device transmission component in the mode of running, and the liquid pool of hydraulic fluid, hydraulic fluid can be pumped into the piston-cylinder assembly from described liquid pool, in order to give a side or the opposite side hydraulic loaded of piston, thereby move described transmission device transmission component according to pumping direction separately.
Although for fear of using mortor operated valve that the alone valve system of hydraulic pressure activation is set in this hydraulic transmission; described valve system is located at piston (terminal) position in the piston-cylinder assembly; it can guarantee the pressure compensation on the piston; in order to alleviate the stressed of transmission device transmission component (shifting fork); even in this case; this formerly technology be considered to expensive because each piston-cylinder assembly of speed changer switching member association needs an independent pump.In addition, each pump must suitably be controlled, so that the piston-cylinder assembly also can move to (neutral) central position.
Goal of the invention
The purpose of this invention is to provide a kind of for driving the especially hydraulic transmission of the one or more positioning elements of motor vehicle transmission, described hydraulic transmission is avoided above-mentioned shortcoming, compare with above-mentioned formerly technology, especially significantly improve whole efficiency and reduce cost.
Summary of the invention
This purpose is to realize by the represented feature of claim 1.Of the present invention useful or to improve easily be the theme of claim 2 to 9.
According to the present invention, a kind of for driving the especially hydraulic transmission of at least one positioning element of motor vehicle transmission, comprise pump, at least one double-acting piston-cylinder assembly, and the liquid pool of hydraulic fluid, the motor-drive pump driver that the pumping direction that has described pump can reverse, described piston-cylinder assembly hydraulic connecting is to pump and piston, described piston-cylinder assembly hydraulically is connected with described pump, and the piston of described piston-cylinder assembly is connected with the formula positioning element with the side of running, described pump can be pumped into the piston-cylinder assembly to hydraulic fluid from this liquid pool, in order to load for described piston hydraulic pressure, be loaded into a side or the opposite side of described piston, thereby according to pumping direction running fix element separately, described piston-cylinder assembly function ground connects the stopping device with locking member, described locking member imposes spring-biased and remains on locked position, prevent that described positioning element from moving, and the actuator that described locking member can be subject to the electric power activation drives and the antagonism spring-biased, make locking member move to the release position from locked position, described positioning element can be moved, wherein, pump driver and actuator are connected electrically to control unit, and the electric power that described control unit is coordinated pump driver and actuator activates action.
Particularly, the coordination of pump driver and actuator is carried out by control unit, at first, the actuator of (each) stopping device is activated by electric power, so that the locked position of locking member from preventing that positioning element from moving when the no current, move to the release position, thus stop or the locking of the positioning element that the cancellation stopping device causes.Then, control unit powers up and activates the pump driver, so that pumping direction as required starts reversible pump, so, act on the hydraulic pressure on the effective working surface of corresponding hydraulic pressure of piston of piston-cylinder assembly, cause that positioning element moves by predetermined direction.Now, in case positioning element arrives desired location, control unit applies electric current with regard to stopping to the actuator of stopping device, and turn-offs the pump driver, and for instance, described desired location can detect by the stroke sensor on the piston-cylinder assembly.So locking member returns its locked position and prevents that positioning element from moving under the spring-biased effect.
Alternatively, the actuator of all right coordinated manipulation pump driver of control unit and one or more sets stopping devices, at first corresponding actuator is activated by electric power, so that by drawing back the stop of locking member cancellation positioning element, then, according to the described pump of pumping direction operation of determining, thereby make positioning element begin to move to predetermined direction, after this, actuator switches to no current state more at once, thereby the locking member of spring-biased is automatically moved to its locked position or reaches the stop purpose, consequently, in case all parts (locking member/positioning element) that participate in action move to its relevant position, described pump just is turned off.In this possibility, do not detect piston position or similarly form be necessary.
Obviously, because only just power to electric component when (each) positioning element need to move, the running of hydraulic transmission aspect the energy that proposes here is highly beneficial, and simultaneously, the expense on technology hardware is quite low, thereby is cheaply.Need hardly any type of storage unit or guiding valve, and the fluid cleanliness level of bringing thus rising, equally do not need complicated pump control yet.In addition, because in order to begin two elements of mobile always necessary activation, that is, the actuator of pump driver and (each) stopping device has advantageously increased Security to prevent wrong activation.The electric power of coordinating the actuator of pump driver and (each) stopping device by control unit activates, it is final so that similar useful mode can be further used for the positioning element piston-cylinder assembly relevant with each, they can be activated by a unique pump hydraulic pressure, like this, those do not need mobile positioning element, be subject to stopping device separately, namely wherein locking member locking remains on no current state.
Generally speaking, stopping device can be provided on separately the positioning element.Yet according to installation requirement separately, described stopping device also can be fixed on the piston-cylinder assembly, and in this case, described locking member matches with locking section on the piston.This being arranged in most cases is first-selected, use and assembly space because saved the assembly fee of positioning element (for example, the speed changer sleeve), and these bulks usually is very compact.
Particularly, the locking section on the piston can be formed by the radial groove of the configuration of axially spaced-apart on the piston periphery.This not only is conducive to production technology, because such radial groove can be formed on the piston in simple mode, and is because piston needn't be protected with anti-rotation.
In the first possibility, piston at the piston-cylinder assembly, but perhaps be the hydraulic pressure load side of the piston of one of a plurality of piston-cylinder assemblies at least, can configure effective working surface of same size, described effective working surface consists of the border of (accordingly) piston-cylinder assembly pressure chamber separately.In this possibility, in order to make (each) piston-cylinder assembly reach the volume balance and to afford redress, namely, in the situation that piston moves, cause the specific hydraulic fluid scale of construction to be transported to one of two pressure chambers, piston is just transferred to another pressure chamber to the hydraulic fluid of same volume.Therefore, needn't take any preventive measure just can be poor from liquid pool liquid draw press liquid for compensation volume.
Otherwise, in the second possibility, the piston of piston-cylinder assembly, but perhaps be the hydraulic pressure load side of the piston of one of a plurality of piston-cylinder assemblies at least, effective working surface with different size, described effective working surface consists of respectively the border of (accordingly) piston-cylinder assembly pressure chamber separately, wherein, being provided with between reversible pump and (separately) piston-cylinder assembly can be by the valve group of pumping pressure hydraulic pressure activation, be used in the situation that piston moves the difference in volume of guaranteeing between the compensatory pressure chamber, this is highly beneficial aspect the energy.Like this, piston only needs the cylinder guidance surface of a constant diameter, extend a piston handle from a side of described piston, described piston handle connects piston and positioning element in the mode of running usually, and the cross section of piston handle reduces the effective working surface of corresponding piston hydraulic pressure; In contrast, in the situation that above-mentioned first possibility, the cylinder guidance surface forms by two sections of different-diameter usually, thereby two running lengths are arranged, in order that " area " of the cross section of compensating piston handle is in order to obtain effective working surface of same area at piston.
If for the electric power of coordinating pump driver and actuator activates and/or needs travel information for other purposes, so, (each) piston-cylinder assembly can comprise the sensor device for detection of piston position, preferably, be arranged on the sensor on the cylinder case and be attached to signal element on the piston.Yet as alternative dispensing means, sensor device also can be configured on the positioning element like that.
In addition, but the actuator that the electric power that provides activates can be electromagnetic actuator, and wherein, described control unit can detect the inductance value of described actuator, in order to determine the position of locking member.Therefore, can obtain the relevant position information of (each) locking member by conceptive simple pattern and mode.In this, the radial groove on the aforesaid piston periphery can have different depths of groove so that detect the inductance value of electromagnetic actuator by control unit, the position axis that also just can determine the piston that the cylinder case is interior to.
At last, further according to concept of the present invention, if drive a plurality of positioning elements, for example, be used for shifting fork or the speed changer sleeve of many gears automatic shifting transmission gear box (AST) of motor vehicle, can configure a plurality of double-acting piston-cylinder assemblies, the piston of described piston-cylinder assembly is connected to separately positioning element in the mode of running respectively, wherein, each piston-cylinder assembly arrives an only pump with the parallel mode hydraulic connecting expediently.
Brief Description Of Drawings
Below will be by preferred embodiment, the present invention will be described in more detail in conjunction with accompanying schematic figure, and in the accompanying drawings, identical label represents same or corresponding parts, and the elastic member major part is simplified shown as not deformation state, wherein:
Figure 1 shows that the circuit diagram for the hydraulic transmission of the positioning element that drives motor vehicle transmission, a piston-cylinder assembly is only arranged, described piston-cylinder assembly is provided with stopping device, is integrated in the case of transmission, as according to the first embodiment of the present invention;
Figure 2 shows that the enlarged view of the detail section II among Fig. 1, how the locking member that illustrates stopping device matches with locking section on the piston of piston-cylinder assembly, and described locking section is formed by the radial groove with different depths of groove in piston peripheral, axial arranged spaced;
Figure 3 shows that in the drawings, the radial groove of piston periphery has the identical degree of depth, is provided with in addition the sensor device for detection of piston position according to the circuit diagram of the variant of the first embodiment's hydraulic transmission;
Figure 4 shows that the circuit diagram for the hydraulic transmission of a plurality of positioning elements that drive motor vehicle transmission, piston-cylinder assembly with respective numbers, described piston-cylinder assembly with the parallel mode hydraulic connecting to single pump, as according to a second embodiment of the present invention;
Figure 5 shows that the circuit diagram of the hydraulic transmission that a piston-cylinder assembly is only arranged, be used for driving the positioning element (with the selector rod of shifting fork) of motor vehicle transmission, wherein, compare with previous embodiment, stopping device is arranged on the positioning element, as a third embodiment in accordance with the invention;
Figure 6 shows that the circuit diagram of the hydraulic transmission that a piston-cylinder assembly is only arranged, be used for driving motor vehicle transmission positioning element (with the selector rod of shifting fork), stopping device is arranged on the described positioning element, wherein, compare with previous embodiment, the piston of piston-cylinder assembly has effective working surface of two different sizes, be used in the situation that piston moves the difference in volume between the pressure chamber of compensating piston-cylinder assembly, as a fourth embodiment in accordance with the invention in the valve group that connects between pump and the piston-cylinder assembly.
In these figure, and in the following description, omitted detailed diagram or explanation to driven positioning element, known because these elements and function thereof are the professional workforces, it is made an explanation obviously there is no need for understanding the present invention.
Embodiment's detailed description
In Fig. 1, label 10 ordinary representations are used for the hydraulic transmission of the positioning element (not shown) of driving motor vehicle transmission, the example of described positioning element is the selector rod with shifting fork or speed change sleeve, in Fig. 1, only be expressed as to partial schematic case of transmission 12, in the example of giving, this case of transmission is divided into a plurality of parts.Below will describe in further detail, described hydraulic transmission 10 comprises pump 14, double-acting piston-cylinder assembly 16, and the liquid pool 20 of hydraulic fluid, pumping direction (the four-headed arrow R among Fig. 1) is arranged described pump 14 therefore the motor-drive pump driver M(that can reverse is called reversible pump), described piston-cylinder assembly hydraulically is connected with pump 14, and the piston 18 of described piston-cylinder assembly is connected with positioning element in the mode of running, described pump 14 can be pumped into piston-cylinder assembly 16 to hydraulic fluid from this liquid pool, in order to load for described piston hydraulic pressure, be loaded into a side (effectively working surface 22) or the opposite side (effectively working surface 24) of described piston 18, thereby according to separately pumping direction R running fix element.It should be noted that, in the example of giving, described piston-cylinder assembly 16 functionally and also is the stopping device 26 that physically connects with locking member 28, described locking member imposes spring-biased and remains on locked position, for example, by means of spiral compression spring 30(as shown in Figure 1), prevent that described positioning element from moving, described locking member can be subject to actuator's 32 drivings that electric power activates, be preferably electromagnetic actuator, and the antagonism spring-biased makes locking member move to the release position from locked position, in order to allow or enable the movement of described positioning element.Particularly, described pump driver M and actuator 32 electric (electricity cable 34) are connected to control unit ECU, the electric power that described control unit is suitably coordinated described pump driver M and described actuator 32 activates action, simply describes such as brief description part of the present invention.
Described pump 14 has two hydraulic connecting ends 36,38, depend on the pumping direction that described control unit ECU is selected or definite, one connects and composes pump intake (suction pipe interface), suck thus or present hydraulic fluid, another connects and composes pump discharge (pressure tube interface), sends thus the hydraulic fluid of pressurization.The type of pump is discussed here, for example, gear pump, roller pump, vane pump and radially or axial piston pump.For present application, just enough if described pump 14 is embodied as constant flow pump, corresponding to the predetermined rotating speed of pump driver M, described constant flow pump provides constant flow.Described pump driver M can arbitrarily control rotating speed, in order to can change, for instance, the given speed of positioning element.Pump driver M is by electricity cable 34 power supplies or activation, and described electricity cable dots in Fig. 1, sets up electrical connection with described control unit ECU.
The hydraulic connecting end 36,38 of pump 14 is connected to liquid pool 20 via suction line 40,42 respectively, is connected with to stop the one- way valve 44,46 that flows to liquid pool 20 directions in described suction line.Described one- way valve 44,46 can be biased to the blocking-up position of liquid pool 20 directions; But this point does not show in the accompanying drawings.In addition, guarantee that the pressure piping 48,50 of setting up hydraulic connecting with piston-cylinder assembly 16 is connected respectively to hydraulic connecting end 36,38.To some degree, obviously to be for the professional workforce, for instance, if the pump among Fig. 1 14 pumping direction R running in a clockwise direction, pump 14 is via hydraulic connecting end 36, from pressure piping 48, and in the example of giving, via one-way valve 44 and suction line 40 from liquid pool 20 inhalant liquid press liquids.Yet pump 14 is carried the hydraulic fluid of pressurization via its another hydraulic connecting end 38 in pressure piping 50.Particularly, one-way valve 46 prevents decline of pressure or prevents that hydraulic fluid is back to liquid pool 20.In similar mode, if the pump among Fig. 1 14 turns round with anticlockwise pumping direction R, the earth pressure release of pressure piping 50 and pressure piping 48 bears pressure, wherein, the hydraulic fluid among Fig. 1 carries or is delivered to the left side of pump 14 from the right side of pump 14.
Pressure piping 48,50 leads to respectively control valve or the pressure tube interface 52,54 of piston-cylinder assembly 16. Pressure tube interface 52,54 is schematically simplified the passage that is expressed as in the case of transmission 12 in Fig. 1, in illustrated embodiment, described pressure tube interface is with two embedded members 56,58, form the cylinder chamber 60 of piston-cylinder assembly 16, the piston 18 in the cylinder chamber is separated two pressure chambers 62,64 mutually.
Embedded member 56,58, preferably use such as polyphthalamide (polyphtalamide, PPA) and so on plastic materials, and predetermined content of glass fiber, for example 50%, make with jet molding method, described embedded member closely inserts the shoulder hole that is associated 66,68 of case of transmission 12, in this embodiment, in the described embedded member 56,58 one, fixedly sleeved on another.Cuff, boss, groove or similar structure in embedded member 56,58 peripheries, form in this example the admittance position of O type circle 70, described O type circle cooperates with the shoulder hole 66 of case of transmission 12,68 inner wall surface, in order to realize the static sealing of piston-cylinder assembly 16 relative external environment conditions.Otherwise, embedded member 56 in Fig. 1 left side is in fact sleeve and bearing shape, its left side leans on the boss of the shoulder hole 66 of case of transmission 12, and the embedded member 58 on Fig. 1 right side is in fact large mouthful of beaker shape, and chuck section 72, base section 74 and extension 76 are arranged; Described base section 74 is near Fig. 1 right sides, and embedded member 58 is by base section, be fixed on the boss of shoulder hole 66 of case of transmission 12, and be the extension 76 of hollow cylindrical in essence, be to link to each other with base section 74 on Fig. 1 right side equally.
The opening of the pressure tube interface 52 on the left of Fig. 1, the approximate pressure chamber 62 that directly enters into embedded member 56 inside.Otherwise the opening at the pressure tube interface 54 on Fig. 1 right side enters annular chamber 78, described annular chamber is around the base section 74 of embedded member 58, its external boundary is subject to case of transmission 12, and interior boundary is subject to embedded member 58, and its border, both sides is subject to the O type circle 70 of intermediate configurations.Between this annular chamber 78 and the pressure chamber 64, setting connects via the fluid of several passages 80 of the base section 74 of embedded member 58, these passages be evenly distributed on embedded member 58 around (referring to the related content of the piston-cylinder assembly 16 that is presented at Fig. 4 top but in sectional view, does not show.
The piston 18 of piston-cylinder assembly 16 is the band handle pistons with piston portion 82 and piston handle 84, equally preferably use such as polyphtalamide(PPA) plastic materials, and predetermined content of glass fiber, for example 50%, make with jet molding method, described be furnished with the shoulder hole 86 that runs through continuously with the handle piston.Shoulder hole 86 is used for hydraulic seal in itself known mode, and the selector rod axial anti-pulling force and the compression resistance reaction that produce, and described selector rod is not presented among Fig. 1, but represents with label 88 in Fig. 5 and Fig. 6.At the state that selector rod has been installed, in Fig. 1, selector rod stops in the position of the end of close piston portion 82, its tight hydraulic lock or with pressure chamber 62 adjacency, and in Fig. 1, it stretches out to the right outside the end that projects to piston handle 84, arrives its external part, for example, 90 represented shifting forks among Fig. 5 and Fig. 6.
At outer circumferential side, piston handle 84 replacedly imports in the sliding sleeve 92, and sliding sleeve 92 is fixed on again in the extension 76 of embedded member 58.At sliding sleeve 92 be fixed between the positioning ring 94 in the base section 74 of embedded member 58 seal element 96 is set, in illustrated embodiment, itself is the ring of known trough of belt, and described seal element 96 cooperates with the outer surface 98 of piston handle 84, to Fig. 1 right side dynamic seal (packing) pressure chamber 64.
Piston portion 82, its diameter is greater than piston handle 84 by contrast, at its outer circumferential side of two ends longitudinally, be respectively equipped with radial groove, be used for holding seal element 100 or 102 separately, in illustrated embodiment, described seal element itself also is the ring of known trough of belt.In this embodiment, the seal element 100 in Fig. 1 left side cooperates with the inner circumferential surface of embedded member 56 to Fig. 1 right side dynamic seal (packing) pressure chamber 62, described pressure chamber 62 take piston 18(with) the selector rod (not shown) is as the boundary.In contrast, the seal element 102 on the piston portion 82 on Fig. 1 right side cooperates with the inner circumferential surface 106 of the chuck section 72 of embedded member 58, to Fig. 1 left side dynamic seal (packing) pressure chamber 64.
Cylinder chamber 60 between seal element 100 and 102 without in the pressure zone, form several locking sections at piston 18, these locking sections match with the locking member 28 of stopping device 26, in illustrated embodiment, described stopping device 26 is fixed on the piston-cylinder assembly 16, referring to following more detailed description.In this, what also will mention is, the locking section on piston be around radial groove 108,110 and 112(see Fig. 2), described radial groove is spaced-apart vertically, is formed on the periphery of the piston portion 82 of piston 18.
In this embodiment, but in two hydraulic pressure load side of piston 18, effective working surface 22,24 of two same sizes of configuration, described effective working surface consists of the pressure chamber 62 of piston- cylinder assembly 16,64 border.This is embedded member 56,58 inner circumferential surface 104,106 diameter D 104, D 106Poor, with the diameter D of perimeter surface 98 outside the piston handle 84 of piston 18 98Coordinate mutually to realize.More precisely, the diameter D that depends on the outer surface 98 of piston handle 84 98, described outer surface 98 cooperates with seal element 96, selects the diameter D of the inner circumferential surface 106 in the embedded member 58 106, make it greater than the diameter D of the inner circumferential surface 104 in the embedded member 56 104Both differences make the circular section of pressure chamber 62 long-pending consistent with the annular cross-sectional area of pressure chamber 64, described inner circumferential surface 106 cooperates with seal element 102, described inner circumferential surface 104 cooperates with seal element 100, the circular section of described pressure chamber 62 long-pending (effective working surface 22 in piston 18 left sides among=Fig. 1) is take inner circumferential surface 104 as the border, and the annular cross-sectional area of described pressure chamber 64 (effective working surface 24 on piston 18 right sides among=Fig. 1) is take outer surface 98 and inner circumferential surface 106 as the border.Importantly, always to afford redress and make piston-cylinder assembly 16 reach the volume balance, for instance, namely, if piston 18 moves to Fig. 1 right side, the hydraulic fluid of certain volume is transported to pressure chamber 62 by pressure tube interface 52, and piston 18 is just transferred to pressure chamber 64 to the hydraulic fluid of same volume by passage 18, annular chamber 78 and pressure tube interface 54, and vice versa.
Stopping device 26 comprises case 114, and in illustrated embodiment, described case is attached to the outside of the embedded member 58 of piston-cylinder assembly 16 by rights.The electromagnetic coil 116 of actuator 32 is accommodated in the case 114, and local at least concentric ring is around ferromagnet locking member 28, and described locking member plays the effect of the moving iron core of electromagnetic driver here.Interchangeable locking member 28 in the mode of similar piston 116 li of electromagnetic coils, pass breach 118,120(sees Fig. 2) engagement, described breach 118,120 is formed in case 114 or the embedded member 58, more precisely in chuck section 72, breach 118,120 aligned with each other, so that stopping projection 122 can with piston portion 82 in radial groove 108,110,112 engagements, described stopping projection 122 is arranged on the lower end of the locking member 28 among Fig. 1, and the cross section of described stopping projection 122 forms slight tapering towards its free end.The upper end of the locking member 28 in Fig. 1 is provided with the perforate 124 for a spiral compression spring 30 of carrying, and described spiral compression spring stretches out from locking member 28, is supported on the case 114.At last, electromagnetic coil 116 is by electricity cable 34 power supplies, and described electricity cable dots in Fig. 1, sets up electrical connection with described control unit ECU.
Obviously, spiral compression spring 30 attempts to promote the case 114 that locking member 28 stretches out stopping device 26, when making electromagnetic coil 116 no current state, rely on spring force, stopping device 122 remain on piston portion 82 on radial groove 108,110, one of 112 engagements.By the accurate coupling in the machine-building process, prevent that piston 18 breaks away from piston-cylinder assemblies 16, even in the situation that pressure chamber 62, one of 64 bears pressure load.In contrast, if electromagnetic coil 116 conductions, the elastic force of the magnetic attraction locking member 28 dipscrews Compress Springs 30 that then produce, make described spring along returning in the case 114 perpendicular to piston 18 movement directions in fact, in this case, stopping projection 122 breaks away from described radial groove 108,110 or 112.Piston 18(and the positioning element that is connected to piston 18 in the mode of running) can move because of the pressure load of corresponding pressure chamber 62 or 64.Each of stopping device 26 (discharging or stop) position, namely locking member 28 is with respect to the position of the case 114 of stopping device 26, can controlled unit ECU inductance value indirect detection by actuator 32 arrive, when locking member 28 moves with respect to case 114, instantaneous air gap is depended in the variation of described inductance value, namely the gap between the close zone of spiral compression spring 30 on locking member 28 and the case 114.
In illustrated embodiment, piston portion 82 is provided with three radial grooves 108,110,112, and axial position and the space of described radial groove on piston 18 limits the special position that is connected to the positioning element of piston 18 in the mode of running.If stopping projection illustrated in figures 1 and 2 122 is set to radial groove 110 engagements with the centre, for instance, this just defines the neutral position of positioning element, in the situation that automatic shifting transmission gear box (ASG), for example, first and third gear between speed change sleeve position, in this case, do not have gear to be in engagement.In contrast, if stopping projection 122 and radial groove 108 or 112 lockings, in the situation that ASG, this has just defined an independent limit positions of positioning element, and for example, speed change sleeve position is engaged in first or third gear.
Other feature according to embodiment illustrated in figures 1 and 2 is that the radial groove 108,110,112 around piston 18 has different depths of groove, especially can see at an easy rate in Fig. 2.If stopping projection 122 is set to and radial groove 108,110, one of 112 engagements, so, the degree of case 114 that locking member 28 stretches out stopping device 26 is larger or less, depends on the degree of depth of each radial groove, and described radial groove produces different air gaps in actuator 32.Therefore, control unit ECU also can judge the axial position of piston 18 in the cylinder case that (especially) embedded member 56,58 forms indirectly by detecting the inductance value of actuator 32.As a result, can obtain the optional additional location information relevant with each position of positioning element.
For example, following operation also can be carried out by aforesaid hydraulic transmission 10, and wherein, control unit ECU in time activates and coordinate the electromagnetic actuator 32 of motor-drive pump driver M and stopping device 26.
If positioning element will be removed from the precalculated position, in this embodiment, described precalculated position is to learn by the inductance value of actuator 32 (indirectly), as mentioned above, for example, central position as depicted in figs. 1 and 2 so, at first will apply electric current to the actuator 32 of stopping device 26 by control unit ECU.Consequently, locking member 28 is resisted the elastic force of spiral compression spring 30 and is retracted under magnetic force, and in this case, each radial groove 110(that stopping projection 122 breaks away from piston 18 is central recess here), thus stopping device discharged.Now, apply electric current by control unit ECU to pump driver M, so, pump 14 pumping direction R as required starts, described pumping direction is to realize that the location movement direction of expection is necessary, and for example, pumping direction R is to the left side of pump 14 from the right side of pump 14 in Fig. 1.Therefore, the hydraulic pressure load appears in pressure chamber 62, the piston 18 among Fig. 1 thereby mobile to the right.After the short shift motion of piston 18 experience, can cut off the power supply to actuator 32, in order to make spiral compression spring 30 attempt to promote locking member 28 among Fig. 1 downwards.In case the piston 18 relevant with locking member 28 puts in place, stopping projection 122 just can slip into radial groove 108.Now, cut off the power supply of pump driver M, system just is in complete no current state again.
Obviously, piston 18 can move to next stop position from a stop position according to this pattern and mode.If positioning element will directly move to another terminal position from a terminal position, namely do not move to central position or neutral position, the electric current that is applied to actuator 32 can be kept one long period, be engaged to before the radial groove 108 or 112 that is in terminal position separately at stopping projection 122, during this period of time so that the radial groove 110 of the centre on the piston 18 " is crossed " telescopic stopping projection 122 not with its stop.
Below with reference to Fig. 3 the modification of previous embodiment is illustrated, the scope of explanation only limits to difference between the two.As the explanation of simplifying, the description of having omitted case of transmission 112 parts among Fig. 3.
In modification shown in Figure 3, there is not difference in the radial groove 108,110 of piston 18 peripheries, 112 depth of groove, but on the contrary, all be processed into the same degree of depth.For this purpose, piston-cylinder assembly 16 comprises sensor device 126, each position for detection of the piston 18 in the piston-cylinder assembly 16, on the cylinder case, more precisely, on the periphery of the embedded member 58 of piston-cylinder assembly 16, suitably a sensor 128 is installed in configuration, for example, well known Hall transducer own, suitably signal element 130 is installed in configuration on piston 18, for example, block permanent magnet in illustrated embodiment, places between the radial groove 108 and 110 on the piston portion 82.Described sensor 128 is connected to control unit ECU by signal cable 132.
In this embodiment, when this system is in no current state, stopping projection 122 on the locking member 28 of stopping device 26, under the effect of the elastic force of spiral compression spring 30, equally also tend to be engaged to the radial groove 108,110,112 on the piston 18, thereby prevent the movement of piston 18.If apply electric current by control unit ECU to the actuator 32 of stopping device 26, the direction that electromagnetic coil 116 just makes progress in Fig. 3 retracts locking member 28, discharge stopping device, that is to say, make stopping projection 122 break away from each radial groove 108,110 or 112 of piston 18.Control unit ECU is control pump driver M at once, so the piston 18 of the load that is under pressure moves along the orientation of expection, described orientation depends on predetermined pumping direction R.In the case, each position of piston 18 is determined by sensor device 126, described sensor 128 is static with respect to piston-cylinder assembly 16, and described sensor device testing signal element 130 is with respect to each relevant position of sensor 128.Moment before piston 18 arrives the stop position of expecting, control unit ECU stops to electromagnetic coil 116 power supplies, so because the elastic force of spiral compression spring 30, locking member 28 is attempted forward, namely the downward direction among Fig. 3 moves.In case the corresponding radial groove 108 on the piston portion 82,110 or 112 is along with being moved further of piston aimed at the stopping projection 122 of locking member 28, stopping projection 122 just slips into described radial groove, so that fixed piston 18 vertically.At last, control unit ECU cuts off the power supply of pump driver M.
Another embodiment of hydraulic transmission 10 can know by inference from Fig. 4, compare with previous embodiment, it is three here that this embodiment configures several double-acting piston-cylinder assembly 16(), the mode that the piston 18 of described piston-cylinder assembly is configured to respectively to turn round is connected to positioning element (not shown) separately.As the explanation of simplifying, again omitted the description of the case of transmission part that piston-cylinder assembly 16 is installed among Fig. 4, only to being illustrated for detection of separately piston position or the sensor device of positioning element position.
According to Fig. 4, the pressure piping 48 that leads to (first) piston-cylinder assembly 16 on Fig. 4 top, 50, branch becomes connecting pipeline 134,136, hydraulic connecting is to the pressure tube interface 52,54 of newly-increased piston-cylinder assembly 16, so that hydraulic operation is parallel-connected to all piston-cylinder assemblies 16 of single pump 14.
Obviously, control unit ECU is by powering to stopping device 26, cancel the piston locking on the piston-cylinder assembly 16 relevant with certain certain position element, and connect pump 14 according to specific pumping direction R, this certain position element just can move according to the orientation of expection, simultaneously, by stopping device associated with it on the function 26, the piston 18 of newly-increased piston-cylinder assembly 16 keeps no current state.By this power supply mode, give simultaneously corresponding stopping device 26 and pump driver M power supply, the piston 18 of be under pressure load, having cancelled locking moves according to same orientation thereupon, just can be according to same orientation mobile several positioning elements simultaneously.
Fig. 5 has showed the another one embodiment of hydraulic transmission 10, here also have with about the similar simplification of the discussion of Fig. 4, the essential distinction of this embodiment and previous embodiment is, described stopping device 26 is not arranged on the piston-cylinder assembly 16, but on the positioning element of reality, here, described positioning element is with the selector rod 88 of shifting fork 90, and this embodiment has reduced piston-cylinder assembly 16 needed installing spaces.Particularly, selector rod 88 is arranged on radial groove 138,140,142 outside, described radial groove cooperates according to the stopping projection 122 on the locking member 28 of the pattern of describing and mode and stopping device 26, can select to make electromagnetic coil 116 no currents and locking, thereby constraint positioning element, and then the piston 18 of confined piston-cylinder assembly 16, perhaps by discharging it to stopping device 26 power supply cancellation lockup states.
At last, Fig. 6 has also showed the another one embodiment of hydraulic transmission 10, compare with previous a few width of cloth figure, Fig. 6 is principle schematic to a greater extent, the essential distinction of this embodiment and previous embodiment is, but the effective working surface 22,24 that has different size in the hydraulic loaded side of piston 18, described effective working surface 22,24 consists of respectively the independent pressure chamber 62 of piston- cylinder assembly 16 or 64 border.In the case, in the outside of piston 18 seal element 144 is only arranged, cooperate with piston-cylinder assembly 16 only cylinder guidance surfaces 146, in order to make pressure chamber 62 and 64 mutual hydraulic isolation, this compares with previous embodiment, has shortened significantly piston-cylinder assembly 16.In the situation that piston 18 moves, in order to ensure the difference in volume between the compensatory pressure chamber 62,64, be provided with a valve group 148 that can be activated by pumping pressure hydraulic pressure between pump 14 and piston-cylinder assembly 16, described difference in volume results from the effective working surface 22 of hydraulic pressure, 24 of different size corresponding to same piston stroke.
In illustrated embodiment, this valve group 148 comprises two pressure controlled two position two-way valves (2-2-wayvalve) 150,152, and two aperture elements (aperture) 154,156, and described two position two-way valve spring-biased in the circulation zero-bit.First two position two-way valve 150 is connected in the connecting pipeline 158 between the pressure piping 48,50, and second two position two-way valve 152 places the pressure piping 50 of self-pumping 14, is positioned at before the connecting pipeline 158.Aperture elements 154 places the pressure piping 48 of self-pumping 14, be positioned at before the connecting pipeline 158, and aperture elements 156 is connected in the hydraulic connecting end 38 and the pressure piping 50 between second two position two-way valve 152 of pump 14.Article one, pilot line 160 is connected on the hydraulic connecting end 36 and the pressure piping 48 between the aperture elements 154 of pump 14, leads to second two position two-way valve 152 in the pressure piping 50, but activates so that its origin comes from the pressure hydraulic pressure of pressure piping 48.Equally, a pilot line 162 is connected on the hydraulic connecting end 38 and the pressure piping 50 between the aperture elements 156 of pump 14, leads to first two position two-way valve 150 in the pressure piping 158, but activates so that its origin comes from the pressure hydraulic pressure of pressure piping 50.
Can the same position in pressure piping 50 arrange one and replace by pilot line 160 and activate in the one-way valve (not shown) towards the direction blocking-up of pump 14, and alternatively with the two position two-way valve 152 of aperture elements 156 combinations.So it is unnecessary that the aperture elements in pressure piping 48 also just becomes.
The operation in this loop is as follows: if pump 14 rotates according to counterclockwise pumping direction R, because the result of aperture elements 154, in pressure piping 48, produce back pressure (back-pressure), pass to two position two-way valve 152 and it is closed by pilot line 160.Yet two position two-way valve 150 stays open, so, because via the result of the hydraulic connecting of connecting pipeline 158, two effective working surfaces 22,24 of piston 18 are by the load of similarly exerting pressure.Because effective working surface 22 in piston 18 left sides among Fig. 1 is larger, piston 18 moves to the right side of Fig. 1, and obviously, hypothesis has been cancelled the locking of selector rod 88 by powering to stopping device 26 here.In this case, from annular pressure chamber 64(right-hand side) the hydraulic fluid scale of construction that shifts is used to fill cylinder pressure chamber 62(left-hand side); Still the hydraulic fluid scale of construction that lacks is presented from liquid pool 20 via one-way valve 46 by pump 14.
In contrast, if the controlled unit ECU control of pump driver M, so that pump 14 would be according to the clockwise pumping direction R delivery hydraulic pressure liquid among Fig. 6, because the result of aperture elements 156 produces back pressure in pressure piping 50.This back pressure conveys to the two position two-way valve 150 in the connecting pipeline 158 and it is closed by pilot line 162.Yet the two position two-way valve 152 in pressure piping 50 stays open.So the annular pressure chamber 64 of piston-cylinder assembly 16 is connected to the flow stream pressure district of pump 14 (hydraulic connecting end 38), and with the liquid of pump 14 stream suction district (hydraulic connecting end 36) isolation.In contrast, the cylinder pressure chamber 62 of piston-cylinder assembly 16 is connected to the liquid stream suction district (hydraulic connecting end 36) of pump 14.Owing to acting on the pressure difference on the piston 18, cause piston 18 mobile to Fig. 6 left side, obviously, suppose stopping device 26 releases that selector rod 88 has been powered here.
The invention discloses a kind of hydraulic transmission that especially in motor vehicle transmission, is used for driving at least one positioning element, comprise pump, at least one connected double-acting piston-cylinder assembly, and the liquid pool of hydraulic fluid, described pump has the reversible motor-drive pump driver of pumping direction, the piston of described piston-cylinder assembly is connected to positioning element in the mode of running, hydraulic fluid can be pumped into the piston-cylinder assembly from described liquid pool, in order to give one or side person's opposite side hydraulic loaded of piston, thereby according to separately pumping direction running fix element.Particularly, described piston-cylinder assembly function ground connects the stopping device with locking member, described locking member is subjected to spring-biased and remains on locked position, prevent that described positioning element from moving, and but described locking member is subject to the actuator that electric power activates and drives, and moves to the release position that allows positioning element to move from locked position.In addition, pump driver and actuator are connected electrically to control unit, and the electric power that described control unit is coordinated these parts activates action.As a result, drive positioning element and can reach at low cost high-caliber whole efficiency.
Label list
10 hydraulic transmissions
12 case of transmissions
14 pumps
16 piston-cylinder assemblies
18 pistons
20 liquid pools
22 effective working surfaces
24 effective working surfaces
26 stopping devices
28 locking members
30 spiral compression springs
32 actuators
34 electricity cables
36 hydraulic connectings
38 hydraulic connectings
40 suction lines
42 suction lines
44 one-way valves
46 one-way valves
48 pressure pipings
50 pressure pipings
52 pressure tube interfaces
54 pressure tube interfaces
56 embedded members
58 embedded members
60 cylinder chambers
62 pressure chambers
64 pressure chambers
66 shoulder holes
68 shoulder holes
70 O type circles
72 chuck sections
74 base section
76 extensions
78 annular chambers
80 passages
82 piston portions
84 piston handles
86 shoulder holes
88 selector rods
90 shifting forks
92 sliding sleeves
94 positioning rings
96 seal elements
98 outer surfaces
100 seal elements
102 seal elements
104 inner circumferential surfaces
106 inner circumferential surfaces
108 radial grooves
110 radial grooves
112 radial grooves
114 cases
116 electromagnetic coils
118 breach
120 breach
122 stopping projections
124 perforates
126 sensor devices
128 sensors
130 signal elements
132 signal cables
134 connecting pipelines
136 connecting pipelines
138 radial grooves
140 radial grooves
142 radial grooves
144 seal elements
146 cylinder guidance surface
148 valve groups
150 two position two-way valves
152 two position two-way valves
154 aperture elements
156 aperture elements
158 connecting pipelines
160 pilot line
162 pilot line
The D diameter
The ECU control unit
M motor-drive pump driver
R pumping direction.

Claims (9)

1. hydraulic transmission (10), in particular for driving the one or more positioning elements (88,90) in the motor vehicle transmission, comprise the liquid pool (20) of pump (14), at least one double-acting piston-cylinder assembly (16) and hydraulic fluid; Described pump (14) has the reversible motor-drive pump driver (M) of pumping direction (R), described piston-cylinder assembly (16) hydraulically is connected with described pump (14), and the piston (18) of described piston-cylinder assembly (16) is with mode and the positioning element (88 of running, 90) connect, hydraulic fluid can be transported to the piston-cylinder assembly by pump (14) from described liquid pool, in order to give a side (effectively working surface 22) or opposite side (the effectively working surface 24) hydraulic loaded of piston (18), thereby according to pumping direction (R) running fix element (88 separately, 90), it is characterized in that, described piston-cylinder assembly (16) functionally connects the stopping device (26) with locking member (28), described locking member is subjected to spring-biased and remains on locked position, prevent described positioning element (88,90) mobile, and but described locking member is subject to actuator (32) driving of electric power activation and resists spring-biased, move to permission positioning element (88 from locked position, 90) mobile release position, wherein, pump driver (M) and actuator (32) are connected electrically to control unit (ECU), and the electric power that described control unit is coordinated pump driver (M) and actuator (32) activates action.
2. according to claim 1 transmission device (10) is characterized in that described stopping device (26) is installed on the described piston-cylinder assembly (16), and wherein, described locking member (28) matches with locking section on the piston (18).
3. according to claim 2 transmission device (10), it is characterized in that locking section on the described piston (18) be by on the piston periphery vertically spaced-apart radial groove (108,110,112) form.
4. according to each described transmission device (10) of aforementioned claim, it is characterized in that described piston (18) but the hydraulic pressure load side on configure effective working surface (22,24) of same size (Fig. 1), described effective working surface consists of respectively the border of the pressure chamber separately (62,64) of piston-cylinder assembly (16).
5. according to claim 1 to each described transmission device (10) of 3, it is characterized in that described piston (18) but the hydraulic loaded side has effective working surface (22 of different size (Fig. 6), 24), described effective working surface consists of respectively the pressure chamber separately (62 of piston-cylinder assembly (16), 64) border, wherein, being provided with between pump (14) and piston-cylinder assembly (16) can be by the valve group (148) of pumping pressure hydraulic pressure activation, and described valve group (148) is guaranteed compensatory pressure chamber (62 when piston (18) is mobile, 64) difference in volume between.
6. according to each described transmission device (10) of aforementioned claim, it is characterized in that described piston-cylinder assembly (16) comprises the sensor device (126) for detection of piston position, described sensor device comprises the sensor (128) that is arranged on the cylinder case and is attached to signal element (130) on the piston (18).
7. according to each described transmission device (10) of aforementioned claim, it is characterized in that but the actuator that described electric power activates is electromagnetic actuator (32), wherein, described control unit (ECU) can detect the inductance value of described actuator (32), in order to determine the position of locking member (28).
8. according to being at least claim 3 or 7 described transmission devices (10), it is characterized in that the radial groove (108,110,112) in the piston periphery has different depth of groove (Fig. 2), so that described control unit (ECU) detects the axial position of piston (18) in the cylinder case by detecting the inductance value of electromagnetic actuator (32).
9. according to each described transmission device (10) of aforementioned claim, it is characterized in that (Fig. 4) configures several double-acting piston-cylinder assemblies (16), the piston of described piston-cylinder assembly (18) is connected to separately positioning element in the mode of running respectively, wherein, described piston-cylinder assembly (16) arrives single pump (14) with the parallel mode hydraulic connecting.
CN201210234535.6A 2011-07-06 2012-07-06 Hydraulic actuation device for actuating positioning members in motor vehicle transmission Active CN102865359B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011107263.6 2011-07-06
DE102011107263A DE102011107263A1 (en) 2011-07-06 2011-07-06 Hydraulic actuating device for the actuation of one or more actuators in particular a motor vehicle transmission

Publications (2)

Publication Number Publication Date
CN102865359A true CN102865359A (en) 2013-01-09
CN102865359B CN102865359B (en) 2015-07-22

Family

ID=46353989

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201210234535.6A Active CN102865359B (en) 2011-07-06 2012-07-06 Hydraulic actuation device for actuating positioning members in motor vehicle transmission

Country Status (8)

Country Link
US (1) US9476431B2 (en)
EP (1) EP2543891B1 (en)
JP (1) JP5763017B2 (en)
CN (1) CN102865359B (en)
DE (1) DE102011107263A1 (en)
ES (1) ES2661692T3 (en)
HK (1) HK1177488A1 (en)
PL (1) PL2543891T3 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103148204A (en) * 2013-03-04 2013-06-12 潍柴动力股份有限公司 Gear cylinder and pneumatic gear actuator
CN106715974A (en) * 2014-07-31 2017-05-24 Fte汽车股份有限公司 Hydraulic or pneumatic operating device for operating actuators in a motor vehicle transmission
CN106795965A (en) * 2014-07-31 2017-05-31 Fte汽车股份有限公司 Device for hydraulically actuating for activating the actuator in motor vehicle transmission
CN107781412A (en) * 2016-08-26 2018-03-09 吉凯恩汽车有限公司 System for hydraulic actuation parking lock
CN108603588A (en) * 2016-01-29 2018-09-28 格特拉格有限两合公司 Gearshift for vehicle transmission
CN108700137A (en) * 2016-01-26 2018-10-23 Fte汽车股份有限公司 Device for activating clutch
CN110219983A (en) * 2018-03-02 2019-09-10 腓特烈斯港齿轮工厂股份公司 Park lock device in vehicle transmission
CN110469669A (en) * 2018-05-09 2019-11-19 Fte汽车有限责任公司 For activating the parking lock module of the parking lock in motor vehicles
CN112912647A (en) * 2018-10-26 2021-06-04 舍弗勒技术股份两合公司 Actuator for a motor vehicle

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011107263A1 (en) 2011-07-06 2013-01-10 Fte Automotive Gmbh Hydraulic actuating device for the actuation of one or more actuators in particular a motor vehicle transmission
DE102012010172A1 (en) * 2012-05-15 2013-11-21 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Actuator assembly for a motor vehicle powertrain
US9803702B2 (en) 2012-07-03 2017-10-31 Fte Automotive Gmbh Hydraulic actuating device for actuation of at least one friction clutch and at least one gear setting element in a motor vehicle
DE102013000157B3 (en) * 2013-01-09 2014-01-23 Fte Automotive Gmbh Hydraulic actuating device for the actuation of at least one friction clutch and at least one transmission actuator in a motor vehicle
DE102013222988A1 (en) * 2013-11-12 2015-05-13 Zf Friedrichshafen Ag Transmission device with multiple translations
JP5894349B1 (en) * 2014-05-30 2016-03-30 三菱重工プラスチックテクノロジー株式会社 Injection molding method, screw, and injection molding machine
DE102015006323B4 (en) * 2015-05-16 2017-04-27 Thomas Magnete Gmbh Parking lock with lock
CN105370881B (en) * 2015-12-07 2018-10-02 上海瑞迪汽车科技有限公司 A kind of two gear shift systems based on double-direction gearpump
DE102016218118B4 (en) 2016-09-21 2018-10-31 Schaeffler Technologies AG & Co. KG Electric pump actuator for actuating a parking lock
DE102016223386A1 (en) * 2016-11-25 2018-05-30 Zf Friedrichshafen Ag Pump system, automatic transmission and motor vehicle
DE102016014523A1 (en) * 2016-12-07 2018-06-07 Fte Automotive Gmbh Electric parking brake actuator for actuating a parking brake in a motor vehicle
DE102017002873A1 (en) * 2017-03-24 2018-09-27 Wabco Gmbh Device and method for detecting the position of a shift fork of a manual transmission
DE102018206275A1 (en) 2018-04-24 2019-10-24 Zf Friedrichshafen Ag Hydraulic actuator for gear shift element
US11280408B2 (en) 2018-12-14 2022-03-22 Svm Schultz Verwaltungs-Gmbh & Co. Kg Locking unit with centre piece
DE102019114559A1 (en) * 2018-12-14 2020-06-18 Svm Schultz Verwaltungs-Gmbh & Co. Kg Locking unit with middle piece
DE102018009852A1 (en) 2018-12-19 2020-06-25 Fte Automotive Gmbh Hydraulic actuating device for actuating actuators in a motor vehicle transmission
DE102018009853B4 (en) 2018-12-19 2022-12-01 Fte Automotive Gmbh Hydraulic actuator for operating actuators in a motor vehicle transmission
DE102019107710A1 (en) * 2019-03-26 2020-10-01 Gkn Automotive Ltd. Switching device for a power transmission element of a motor vehicle
DE102019111240A1 (en) * 2019-04-30 2020-11-05 Svm Schultz Verwaltungs-Gmbh & Co. Kg Locking unit and procedure
DE102022111230A1 (en) * 2022-05-05 2023-11-09 Svm Schultz Verwaltungs-Gmbh & Co. Kg Locking arrangement with electric motor, locking unit and method for operating a locking arrangement
CN117780812A (en) * 2022-09-22 2024-03-29 福缔汽车（太仓）有限公司 Hydraulic actuator, clutch comprising same and vehicle
DE102023001685B3 (en) 2023-04-27 2024-06-20 Mercedes-Benz Group AG Shifting device for a transmission of a motor vehicle, transmission for a motor vehicle and motor vehicle

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996012108A1 (en) * 1994-10-13 1996-04-25 Applied Power Inc. Hydraulic operating device and gearbox provided with such an operating device
DE69315959D1 (en) * 1992-11-16 1998-02-05 Eaton Corp Locking mechanism for drive axle differential
CN101149110A (en) * 2007-10-31 2008-03-26 长沙航空工业中南传动机械厂 Solenoid valve controlled pneumatic gear shifting device
CN101344168A (en) * 2008-08-18 2009-01-14 重庆大学 Hydraulic change gear device of mechanical automatic speed transmission
CN201202804Y (en) * 2008-04-29 2009-03-04 张风果 Automobile reverse gear controller
CN101529132A (en) * 2006-10-19 2009-09-09 腓特烈斯港齿轮工厂股份公司 Device for actuating a gearwheel, which is designed as a loose wheel, of a transmission device
CN101565040A (en) * 2008-04-04 2009-10-28 通用汽车环球科技运作公司 Hydraulic control for a park by wire system used in a multimode hybrid transmission

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6115291Y2 (en) 1981-03-31 1986-05-13
JPH0720443Y2 (en) 1988-09-30 1995-05-15 いすゞ自動車株式会社 2 piston type 3 position cylinder neutral position control device
US5048656A (en) * 1990-08-29 1991-09-17 Eaton Corporation Fluid operated clutch control system having latch member
DE4215721A1 (en) 1992-05-13 1993-11-18 Bosch Gmbh Robert Cold start device for fuel injection pumps
DE4309901B4 (en) 1992-11-10 2010-07-01 Zf Sachs Ag Hydraulic actuator - especially for a motor vehicle friction clutch
WO1997010456A2 (en) 1995-09-12 1997-03-20 Luk Getriebe-Systeme Gmbh Motor vehicle with a device for actuating the torque-transmission system and the gearbox
US5850898A (en) 1995-09-15 1998-12-22 Fahrzeugtechnik Ebern Gmbh Method and device for the hydraulic actuation of a clutch, especially for automobiles
DE19900852A1 (en) * 1998-01-16 1999-07-22 Atlas Fahrzeugtechnik Gmbh Automatically operated gearbox e.g. for vehicle
US6234060B1 (en) * 1999-03-08 2001-05-22 Lord Corporation Controllable pneumatic apparatus including a rotary-acting brake with field responsive medium and control method therefor
DE19950443A1 (en) 1999-05-11 2000-11-30 Siemens Ag Electronic-hydraulic control device for transmissions of vehicles, preferably of motor vehicles
EP1177393B1 (en) 1999-05-11 2003-01-22 Siemens Aktiengesellschaft Electronic-hydraulic control device for gearboxes of vehicles, preferably motor vehicles
DE19949514C2 (en) * 1999-10-14 2001-10-18 Bosch Gmbh Robert Device for rapid pressure build-up in a motor vehicle device supplied with a pressure medium by a feed pump
FR2806671B1 (en) * 2000-03-24 2002-05-31 Renault DEVICE FOR HYDRAULICALLY CONTROLLING GEAR CHANGES OF A MOTOR VEHICLE GEARBOX
DE10360611A1 (en) 2003-12-19 2005-07-21 Fte Automotive Gmbh & Co. Kg Hydraulic function block
AT8987U1 (en) 2005-09-30 2007-03-15 Magna Drivetrain Ag & Co Kg HYDRAULIC SYSTEM FOR CONTROLLING TWO ACTUATORS AND TRANSMISSIONS WITH SUCH A
DE102006008157A1 (en) * 2006-02-22 2007-09-06 Sick Ag Magnetic sensor
DE102007028827A1 (en) 2007-06-20 2009-02-19 Stabilus Gmbh Piston-cylinder assembly
DE102008011898A1 (en) 2008-02-29 2009-09-03 Daimler Ag switching device
DE102011105648A1 (en) 2011-06-07 2012-12-13 Fte Automotive Gmbh Hydraulic actuator for the actuation of clutches in particular a multi-clutch transmission for motor vehicles
DE102011107263A1 (en) 2011-07-06 2013-01-10 Fte Automotive Gmbh Hydraulic actuating device for the actuation of one or more actuators in particular a motor vehicle transmission

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69315959D1 (en) * 1992-11-16 1998-02-05 Eaton Corp Locking mechanism for drive axle differential
WO1996012108A1 (en) * 1994-10-13 1996-04-25 Applied Power Inc. Hydraulic operating device and gearbox provided with such an operating device
CN101529132A (en) * 2006-10-19 2009-09-09 腓特烈斯港齿轮工厂股份公司 Device for actuating a gearwheel, which is designed as a loose wheel, of a transmission device
CN101149110A (en) * 2007-10-31 2008-03-26 长沙航空工业中南传动机械厂 Solenoid valve controlled pneumatic gear shifting device
CN101565040A (en) * 2008-04-04 2009-10-28 通用汽车环球科技运作公司 Hydraulic control for a park by wire system used in a multimode hybrid transmission
CN201202804Y (en) * 2008-04-29 2009-03-04 张风果 Automobile reverse gear controller
CN101344168A (en) * 2008-08-18 2009-01-14 重庆大学 Hydraulic change gear device of mechanical automatic speed transmission

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103148204A (en) * 2013-03-04 2013-06-12 潍柴动力股份有限公司 Gear cylinder and pneumatic gear actuator
CN106715974A (en) * 2014-07-31 2017-05-24 Fte汽车股份有限公司 Hydraulic or pneumatic operating device for operating actuators in a motor vehicle transmission
CN106795965A (en) * 2014-07-31 2017-05-31 Fte汽车股份有限公司 Device for hydraulically actuating for activating the actuator in motor vehicle transmission
CN106715974B (en) * 2014-07-31 2019-03-08 Fte汽车股份有限公司 For activating the hydraulic or pneumatic actuator of multiple setting elements in motor vehicle transmission
CN106795965B (en) * 2014-07-31 2019-07-23 Fte汽车股份有限公司 For activating the device for hydraulically actuating of multiple setting elements in motor vehicle transmission
CN108700137B (en) * 2016-01-26 2020-03-13 Fte汽车股份有限公司 Device for actuating a clutch
CN108700137A (en) * 2016-01-26 2018-10-23 Fte汽车股份有限公司 Device for activating clutch
CN108603588A (en) * 2016-01-29 2018-09-28 格特拉格有限两合公司 Gearshift for vehicle transmission
CN108603588B (en) * 2016-01-29 2023-02-28 格特拉格有限两合公司 Shifting device for a motor vehicle transmission
CN107781412A (en) * 2016-08-26 2018-03-09 吉凯恩汽车有限公司 System for hydraulic actuation parking lock
US10435001B2 (en) 2016-08-26 2019-10-08 Gkn Automotive Ltd. Hydraulic activation of a parking lock
CN107781412B (en) * 2016-08-26 2020-03-20 吉凯恩汽车有限公司 System for hydraulically actuating a parking lock
CN110219983A (en) * 2018-03-02 2019-09-10 腓特烈斯港齿轮工厂股份公司 Park lock device in vehicle transmission
CN110469669A (en) * 2018-05-09 2019-11-19 Fte汽车有限责任公司 For activating the parking lock module of the parking lock in motor vehicles
CN112912647A (en) * 2018-10-26 2021-06-04 舍弗勒技术股份两合公司 Actuator for a motor vehicle

Also Published As

Publication number Publication date
JP5763017B2 (en) 2015-08-12
DE102011107263A1 (en) 2013-01-10
CN102865359B (en) 2015-07-22
US20130008156A1 (en) 2013-01-10
JP2013064493A (en) 2013-04-11
EP2543891A2 (en) 2013-01-09
HK1177488A1 (en) 2013-08-23
US9476431B2 (en) 2016-10-25
EP2543891B1 (en) 2017-12-27
EP2543891A3 (en) 2014-04-02
EP2543891A8 (en) 2013-03-20
PL2543891T3 (en) 2018-04-30
ES2661692T3 (en) 2018-04-03

Similar Documents

Publication Publication Date Title
CN102865359B (en) Hydraulic actuation device for actuating positioning members in motor vehicle transmission
CN103912678B (en) Device for hydraulically actuating
CN101310429B (en) Linear actuator
CN101354079B (en) Actuation system for a servo-assisted mechanical transmission with oil leakage recovery
KR102345868B1 (en) Gearbox control system
CN105102814B (en) Valve cell includes the fluid-working machines device of valve cell
CN103195918B (en) Hydraulical shifting device for an automatic transmission
CN102563052B (en) Control system and method for a dual clutch transmission
CN101387343B (en) Valve control system
CN102162521B (en) Hydraulic control system for a dual clutch transmission
US9803702B2 (en) Hydraulic actuating device for actuation of at least one friction clutch and at least one gear setting element in a motor vehicle
CN101260938A (en) Automobile electric control mechanical type automatic speed variator hydraulic system and its control method
CN102777512A (en) Space wedge type centrifugal clutch capable of rapidly acting, dual clutch transmission with clutch and operation method thereof
CN103968048B (en) Gearbox for motor vehicles
US8434381B2 (en) Transmission for a motor vehicle
CN101027510A (en) Transmission and shift method
CN102177373A (en) Self-retaining target assembly
CN109070725A (en) Utilize the transmission system actuator of the mobile actuator output link of the energy of storage
CN103047409A (en) Device for storing hydraulic fluid
CN103697156B (en) Pneumatic shifting multipoint soft positioning mechanism
CN201526550U (en) Direct-action two-position four-way proportional relief pressure valve
CN104053900A (en) Hydraulic actuation unit, particularly for controlling starting and stopping of hydraulic motors
CN102444631A (en) Latching assembly for energy accumulator
CN106687720B (en) Speed changer for motor vehicle
CN201092989Y (en) Digital direct travel range electrohydraulic actuator

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
REG Reference to a national code

Ref country code: HK

Ref legal event code: DE

Ref document number: 1177488

Country of ref document: HK

C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
REG Reference to a national code

Ref country code: HK

Ref legal event code: GR

Ref document number: 1177488

Country of ref document: HK